U.S. patent number 9,115,816 [Application Number 12/716,456] was granted by the patent office on 2015-08-25 for check valve with modulation and/or anti-oscillation feature.
This patent grant is currently assigned to JIFFY-TITE COMPANY, INC.. The grantee listed for this patent is James Caroll, Michael A. Lenartowicz, James Messecar, Arthur Murray, Kip R. Steveley, Steven Zillig. Invention is credited to James Caroll, Michael A. Lenartowicz, James Messecar, Arthur Murray, Kip R. Steveley, Steven Zillig.
United States Patent |
9,115,816 |
Steveley , et al. |
August 25, 2015 |
Check valve with modulation and/or anti-oscillation feature
Abstract
A check valve includes a modulation and/or anti-oscillation
feature which, in one aspect, modulates the position of the check
valve ball relative to the valve seat to maintain the ball in a
continuous flow position allowing pressurized fluid flow past the
ball while preventing contact between the ball and the valve seat.
In another aspect, an increased mass is selectively coupled to or
forms a part of the movable valve member to dampen oscillations of
the movable valve member in an open fluid flow position without
contact with the valve seat.
Inventors: |
Steveley; Kip R. (Rochester
Hills, MI), Zillig; Steven (Clarence, NY), Murray;
Arthur (Medina, NY), Messecar; James (Wyoming, NY),
Lenartowicz; Michael A. (Jamesville, NY), Caroll; James
(Novi, MI) |
Applicant: |
Name |
City |
State |
Country |
Type |
Steveley; Kip R.
Zillig; Steven
Murray; Arthur
Messecar; James
Lenartowicz; Michael A.
Caroll; James |
Rochester Hills
Clarence
Medina
Wyoming
Jamesville
Novi |
MI
NY
NY
NY
NY
MI |
US
US
US
US
US
US |
|
|
Assignee: |
JIFFY-TITE COMPANY, INC.
(Lancaster, NY)
|
Family
ID: |
42200827 |
Appl.
No.: |
12/716,456 |
Filed: |
March 3, 2010 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20100224258 A1 |
Sep 9, 2010 |
|
Related U.S. Patent Documents
|
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
61157277 |
Mar 4, 2009 |
|
|
|
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F16K
15/044 (20130101); F16K 47/023 (20130101); Y10T
137/0379 (20150401); Y10T 137/7936 (20150401); Y10T
137/7928 (20150401) |
Current International
Class: |
F16K
15/04 (20060101); F16K 47/02 (20060101) |
Field of
Search: |
;137/514.5,539.5,540,543.13,901,543.17,543.19,539
;251/322,323,333,337 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
3901032 |
|
Feb 1990 |
|
DE |
|
0135140 |
|
Mar 1985 |
|
EP |
|
1681500 |
|
Jul 2006 |
|
EP |
|
870631 |
|
Jun 1961 |
|
GB |
|
12045773 |
|
Feb 2000 |
|
JP |
|
WO2006069072 |
|
Jun 2006 |
|
WO |
|
WO2009012311 |
|
Jan 2009 |
|
WO |
|
Other References
Communication Pursuant to Rule 69 EPC dated Sep. 13, 2010 for
European Application No. 10155019.2. cited by applicant .
International Search Report issued Jan. 6, 2009 for
PCT/US2008/070179. cited by applicant .
Written Opinion of the International Search Authority issued Jan.
5, 2009 for PCT/US2008/070179. cited by applicant .
European Search Report Application No. EP 10 15 5019 completed Jul.
1, 2010. cited by applicant.
|
Primary Examiner: Lee; Kevin
Assistant Examiner: Nichols; P. Macdade
Attorney, Agent or Firm: Young Basile Hanlon &
MacFarlane P.C.
Parent Case Text
CROSS REFERENCE TO CO-PENDING APPLICATION
This application claims the priority benefit to the filing date of
co-pending U.S. Provisional Patent Application Ser. No. 61/157277
filed on Mar. 4, 2009, for Check Valve With Modulation and/or Anti
Oscillation Feature, the entire contents of which are incorporated
herein in its entirety.
Claims
What is claimed is:
1. A fluid flow bypass apparatus comprising: a housing adapted to
be coupled to a structure having a fluid requiring cooling, the
housing having inlet and outlet ports, the housing further having
first and second passageways in communication with the inlet and
outlet ports and a transverse passageway extending between the
first and second passageways the first passageway extending from
one inlet port to one outlet port and the second passageway
extending towards another outlet port from another inlet port; a
check valve disposed in the transverse passageway to insure one way
flow of fluid through the transverse passageway between the first
and second passageways; a valve disposed in one of the first and
second passageways; a thermal actuator engageable with the valve to
move the valve to a position blocking fluid flow through the one of
the first and second passageways until sensing a predetermined
fluid temperature; a valve seat disposed in a bore in the
transverse passageway; a movable member disposed in the bore; a
biasing member engaged with the movable member and acting to
normally bias the movable member into engagement with the valve
seat; the bore having a diameter substantially the same as an outer
diameter of the movable body extending from the valve seat for a
first distance defining a first zone for movement of the movable
member away from the valve seat without substantial fluid flow
through the first zone past the movable member; a second zone
extending from the end of the first zone for a second distance
defining a modulated flow zone where the movable member is biased
away from contact with the valve seat by a volume of fluid flowing
through the first zone into the second zone past the movable
member, the second zone having an increasing cross-section through
the second distance of the second zone.
2. The apparatus of claim 1 comprising: the bore having a diameter
substantially the same as an outer diameter of the movable member
extending from the valve seat for the first distance extending from
the valve seat at least substantially to an opposite outermost
portion of the movable member when the movable member is engaged
with the valve seat defining the first zone.
3. The apparatus of claim 2 wherein: at least a portion of the
second zone has a larger diameter than a diameter of the first
zone.
4. The apparatus of claim 2 wherein: the second zone includes at
least one fluid flow passageway portion having a larger diameter
than a portion of the bore extending through the second zone.
5. The apparatus of claim 2 further comprising: the second zone
defined by flow path extending from an end of the first zone to an
outlet.
6. The apparatus of claim 2 wherein: the first zone has a
substantially constant diameter through at least the first
distance.
7. The of claim 2 further comprising: an insert adapted to be
mounted in the fluid flow bore, the insert carrying the movable
member, the biasing member and the first and second zones.
8. The check valve of claim 7 wherein: the valve seat integrally
carried in the insert.
9. The apparatus of claim 2 further comprising: a rod movably
disposed within the bore for axial movement, the rod coupled to the
movable member.
10. The apparatus assembly of claim 9 further comprising: an
enlarged head coupled to the rod; the biasing member acting on the
head to urge the head toward the movable member to move the movable
member into engagement with the valve seat in a normally closed
fluid blocking position, the movable member and the head formed as
separate members.
11. The apparatus of claim 10 further comprising: the head having a
surface configured to capture a portion of the movable member to
cause axial movement of the movable member, the movable member and
the head formed as a unitary mass within the bore.
12. The apparatus assembly of claim 9 wherein the movable member
further comprises: a head joined to the rod, the head having a
surface engageable with the valve seat.
Description
BACKGROUND
The present invention relates to check valves and also to check
valves used in cooler bypass assemblies which only permit fluid
flow to a cooler when the temperature of the fluid is above a
certain temperature.
Check valves are mounted in bores in a housing or other element and
have a movable member, such as a ball, which is movable into and
out of engaged sealing engagement with a valve seat formed in the
bore to open or close off fluid flow through the bore while
allowing the fluid, when flowing, to flow in only one direction
through the bore. A spring exerts a biasing force on the movable
member or ball to normally bias the ball into engagement with the
valve seat to close off fluid flow through the bore.
When the fluid pressure in the bore increases to a magnitude
greater than the spring force, the fluid pressure overcomes the
spring force and moves the ball away from the valve seat. This
opens the bore to through flow of fluid from the bore inlet to the
bore outlet. When the fluid pressure decreases below the spring
force, the spring moves the ball back into engagement with the
valve seat to close off fluid flow through the bore.
However, oscillation of the movable member or ball can occur when
the ball rapidly reciprocates into and out of engagement with the
valve seat creating objectionable noise and valve chatter. This
occurs just after the ball disengages from the valve seat as fluid
flow past around the ball creates a momentary pressure equalization
on both sides of the ball. This momentary pressure equalization
relieves the pressure acting to force the ball against the spring
and allows the spring to move the ball back toward the valve seat.
The reciprocating movement of the ball into and out of engagement
with the valve seat causes in the objectionable valve chatter.
It would be desirable to provide a check valve which minimizes
valve chatter resulting from oscillation of the movable valve
member into and out of engagement with the valve seat; while still
enabling proper operation of the check valve.
SUMMARY
A check valve is disclosed that is usable by itself in fluid
applications and fluid components to define one-way fluid flow
through a bore or through a transverse or bypass passageway in a
bypass cooler assembly. The valve includes a valve seat, a movable
valve body and a spring which engages the body to normally bias the
body into sealing engagement with the valve seat. An oscillation
dampening construction acts to dampen oscillation of a movable
member when the movable member is in a fluid flow allowing position
relative to the valve seat.
In one aspect, the oscillation dampening construction includes a
bore having substantially the same diameter as an outer diameter of
the movable valve body. The bore extends from the valve seat for a
first distance and defines a first no-leak zone for movement of the
movable body away from the valve seat without substantial fluid
flow through the first distance of the bore. A second modulation
zone extends from the end of the first distance for a second
distance defining a modulated flow zone for the movable body where
the movable body is biased away from contact with the valve seat by
a volume of fluid flowing through the first distance into the
second distance past the movable valve body.
In another aspect, at least a portion of the second modulation zone
has a larger diameter than a diameter of the first no-leak
zone.
In yet another aspect, the second modulation zone includes at least
one fluid flow passageway having a larger diameter than a fluid
flow bore extending through the second modulation zone.
In another aspect, the second modulation zone has at least one flow
passage of increasing diameter through the second distance.
In another aspect, the second modulation zone is defined by a flow
path extending from the passageway to an outlet.
In another aspect, the first zone has a substantially constant
diameter through at least the first distance.
In another aspect, an insert is adapted to be mounted in the
passage way. The insert carries the movable body, the spring, and
the oscillation dampening construction. A valve seat may be
integrally carried in the insert.
In another aspect, the oscillation dampening construction is
carried in a valve housing which also carries the valve seat, the
removable body, the biasing member and the fluid flow passage.
The check valve, in another aspect is, provided with an increased
mass feature which dampens oscillations of the movable member or
ball of the check valve in all directions in the fluid flow bore. A
piston rod is mounted in a bore in a spring retainer carried in the
fluid flow bore of a housing. A spring is seated between the spring
retainer and a piston mounted on the piston rod to bias the piston
into contact with the movable valve member to normally bias the
movable valve member into sealed engagement with the valve seat to
block fluid flow through the bore. When the fluid flow pressure
exceeds the spring force, the fluid urges the movable valve member
and piston away from the valve seat allowing fluid to flow over the
movable valve member and into the fluid bore. In another aspect,
the movable valve member and the piston are integrated with the
piston rod into a unitary structure.
The increased mass provided by the engagement of the piston and
piston rod with the movable valve member dampens oscillations of
the movable valve member to maintain the movable valve member in
the open fluid flow position without contact with the valve
seat.
It would be desirable to provide a cooler bypass assembly which can
be connected to machinery which has fluid which may need to be
cooled, and to the cooler lines which uses the described check
valve.
BRIEF DESCRIPTION OF THE DRAWING
The various features, advantages and other uses of the present
invention will become more apparent by referring to the following
detailed description and drawing in which:
FIG. 1 is an isometric view of a cooler bypass apparatus;
FIG. 2 is a side view of the apparatus this view further showing a
cooler, and cooler lines;
FIG. 3 is a bottom view of the apparatus;
FIG. 4 is a sectional view through the casting to which various
parts are assembled to form the assembly, this view being taken
generally along the line 4-4 in FIG. 5;
FIG. 5 is another sectional view through the casting, this view
being taken generally along the line 5-5 in FIG. 3;
FIG. 6 is an enlarged detail of a portion of FIG. 5;
FIG. 7 is a section taken generally along the line 7-7 in FIG.
5;
FIG. 8 is a sectional view of the assembly shown in FIG. 1;
FIG. 9 is an exploded view of the assembly;
FIG. 10 is a view of a coupling subassembly indicated at SA.sub.1
in FIG.;
FIG. 11 is a view of a coupling subassembly indicated at SA.sub.2
in FIG. 9;
FIG. 12 is an isometric view of the spring and ball guide shown in
FIG. 9;
FIG. 13A is a cross sectional view showing another aspect of a
check valve usable in a cooler bypass apparatus or in other
applications;
FIG. 13B is a graph depicting fluid flow versus check valve ball
position;
FIG. 13C is an enlarged side cross section view showing the valve
body in the modulation zone;
FIG. 13D is lateral cross section view generally taken along line
13D-13D in FIG. 13A;
FIG. 14 is a perspective, partially transparent view showing
another aspect of a cooler bypass apparatus valve;
FIG. 15 is a cross sectional view generally taken along lines 15-15
in FIG. 14;
FIG. 16A is an end view of the valve shown in FIG. 14;
FIG. 16B is a longitudinal cross sectional view generally taken
along line 16B-16B in FIG. 16A;
FIG. 17 is a longitudinal cross sectional view showing another
aspect of a check valve;
FIG. 18 is a cross sectional view showing another aspect of a check
valve;
FIG. 19 is a cross sectional view showing yet another aspect of a
check valve;
FIG. 20 is an end view of the check valve shown in FIG. 19;
FIG. 21 is a cross sectional view of yet another aspect of a check
valve;
FIG. 22 is an end view of the check valve and valve housing shown
in FIG. 21;
FIG. 23 is a cross sectional view of another aspect of a check
valve;
FIG. 24 is an exploded, perspective view of another aspect of a
check valve;
FIG. 25 is a longitudinal cross sectional view of the assembled
check valve and cooler bypass assembly shown in FIG. 24;
FIG. 26 is a longitudinal cross sectional view of another aspect of
the check valve shown in FIGS. 26 and 27.
FIG. 27 is an exploded, perspective view of another aspect of a
check valve used in a cooler bypass application; and
FIG. 28 is an exploded side view of another aspect of a check
valve, valve spring and valve check.
DETAILED DESCRIPTION
With reference to FIGS. 1-9, a cooler bypass assembly is depicted,
by example, and includes an aluminum casting or bypass mounting
plate or housing indicated generally at 10 to which first and
second fluid line coupling subassemblies SA.sub.1 and SA.sub.2 are
secured, along with various other components. The casting 10 is
provided with a relatively flat bottom surface 10.1 which may be
secured to a corresponding flat surface on the machinery which
carries a fluid that needs to be cooled. In order to insure a
non-leak connection the casting 10 is provided with a groove 10.2
(FIG. 3) on its bottom surface which receives an O-ring 20. In
order to secure the casting to the machinery, a plurality of bolt
holes 10.3 are provided through which bolts (not shown) may pass to
secure the casting 10 to the machinery (not illustrated).
It will be understood, however, that the casting or housing 10 can
be a stand alone unit which is coupled to the fluid carrying
machinery by pipes or conduits or by quick connectors to pipes
and/or fastened to an available surface near the fluid carrying
machinery. The casting 10 is provided with two generally vertical
passageways 10.4 and 10.5 and a transverse connecting passageway
10.6. As can best be seen from FIG. 4, the first vertical
passageway 10.4 has an inlet port 10.7 which is adapted to be
aligned with an outlet port in the machinery, and has a threaded
outlet port 10.9 which is adapted to receive the first fluid line
coupling subassembly SA.sub.1. The second passageway has an outlet
port 10.8 which is also adapted to be aligned with a corresponding
port in the machinery to which the casting is secured. The second
passageway also has a threaded inlet port 10.10 which is adapted to
receive the second fluid line coupling subassembly SA.sub.2. Each
of the first and second passageways is adapted to be connected with
a cooler through the fluid line coupling subassemblies SA.sub.1 and
SA.sub.2 to cooler lines, which have special end portions L.sub.1
and L.sub.2, respectively. Each of the end portions is generally
tubular, but is provided with an outwardly extending abutment or
ferrule. The quick connect couplers will be described below. As can
best be seen from FIGS. 6 and 7 the transverse passageway has first
and second portions 10.61 and 10.62 of differing diameters to one
side of the vertical passageway 10.5, passageway 10.61 being of a
larger diameter than passageway 10.62, there being a seat 10.63
between the passageways 10.61 and 10.62 to receive a ball check
valve. As can best be seen from FIG. 6, the larger diameter portion
10.61 is provided with inwardly extending ribs 10.61a which act as
ball guides, but which do not restrict fluid flow. The passageway
also has a further large diameter portion 10.64 which extends from
the vertical passageway 10.5 to the exterior of the aluminum
casting, the end portion being threaded as at 10.65 in FIG. 4.
Mounted within the housing are various subassemblies. The first of
these subassemblies includes a check valve in the form of a movable
element or body 12, such as a ball, a cylindrical piston or other
shaped element, a spring 14 to normally force the ball 12 into the
valve seat 10.63, and ballcheck retainer 16 best illustrated in
FIGS. 8 and 9. The movable body 12 will be described as a ball, for
example only The retainer 16 is provided with a relatively large
diameter end portion 16.1, a relatively small diameter end portion
16.2 which is adapted to be disposed within the spring 14, flutes
16.3 which are adapted to bear against one end of the compression
spring 14, and a small diameter intermediate portion disposed
between the flutes 16.3 and the large diameter portion 16.1. It can
be seen from an inspection of FIG. 8 that the large diameter
portion 16.1 is adapted to be disposed within the larger diameter
portion 10.64 of the passageway 10.6, and the small diameter
portion 16.2 is adapted to lie across the passageway 10.5 so that
flow through passageway 10.5 will not be impeded.
Associated with this check valve subassembly 12, 14, 16 is a plug
subassembly which includes plug 18 and O-ring 21. When the parts
are assembled, and then there is no fluid flow within the housing,
the plug 18 and associated O-ring 21 will be screwed into the
normally open end 10.65 of the passageway 10.6, the plug 18 and
O-ring 21 closing the end of the passageway so no fluid can pass
out of the housing though the passageway 10.6. As seen in FIG. 8,
the right hand end of the plug 18 will bear against the left hand
end 16.1 of the retainer 16. The left hand end of the spring 14
will pass over the small diameter right-hand end 16.2 of the
retainer 16, and will be held in compression, with the right hand
end of the spring forcing the ball 12 towards and into contact with
the seat 10.63 when there is no fluid pressure within the assembly.
At the same time the left hand end of the spring will bear against
the flutes 16.3 of the retainer. When the ball is against the seat
10.63, there is no flow through the passageway 10.6. However, when
the pressure within passageway 10.4 to the right of the ball 12, as
viewed in FIG. 8, is greater than the spring force, the ball will
be forced off its seat permitting flow from the first vertical
passageway 10.4, through the smaller diameter passageway 10.62,
past the seat, then into and through the larger diameter passageway
10.61, and finally into the other vertical passageway 10.5. The
flutes 16.3 of the ballcheck retainer 16 will permit unimpeded flow
of fluid past the flutes.
The first fluid line coupling subassembly SA.sub.1 is best
illustrated in FIG. 10. This coupling assembly is similar to the
female coupling assembly shown in U.S. Pat. No. 4,640,534, the
subject matter of which is incorporated herein by reference
thereto. Thus, the subassembly SA.sub.1 has a principal body 28
having a fluid passageway 24.4 extending through it, a first O-ring
30, a spring clip 32, and a second O-ring 34. The body 28 has a
threaded end portion 28.1 which is screwed into the threaded port
10.10. The body 28 also has an enlarged portion 28.2, hexagonal in
cross section, which may be engaged by a wrench or the like for the
purpose of screwing it into the port 10.10. The O-ring 34 is
received in a groove (no number) between the threaded portion 28.1
and the hex portion 28.2 to insure a leak-tight seal when
assembled. The body is further provided with groove 28.3 adjacent
the end spaced away from the threaded end, the groove having
suitable apertures so that it may receive the spring clip 32. The
passageway 28.4 of the body of the female coupler is provided with
a groove 28.5 which receives O-ring 30. When the cooler line end
portion is fully inserted into the fluid line coupling assembly,
the spring clip will engage on side of the abutment on the cooler
line end portion to prevent it from being withdrawn, and the O-ring
30 will hear against the tubular portion to prevent leakage.
The second fluid line coupler assembly SA.sub.2 is best shown in
FIGS. 8 and 11. This assembly includes a coupler subassembly
similar to the coupler assembly SA.sub.1, a ball check valve
subassembly, and a thermal actuator. The coupler subassembly
includes a principal body 38 having a fluid passageway extending
through it, a first O-ring 40, a spring clip 42, and a second
O-ring 44. The body has a threaded end portion 38.1 which is
screwed into the threaded port 10.9. The body 38 also has an
enlarged portion 38.2, hexagonal in cross section which may be
engaged by a wrench or the like for the purpose of screwing it into
the port 10.10. The O-ring 44 is received in a groove between the
threaded portion 38.1 and the hex portion 38.2 to insure a
leak-tight seal when assembled. The body 38 is further provided
with a groove 38.3 adjacent the end spaced away from the threaded
end, the groove 38.3 having suitable apertures so that it may
receive the spring clip 42. The passageway 38.4 of the body 38 of
the coupler is provided with a groove 38.5 which receives O-ring
40. When the cooler line end portion L.sub.1 is fully inserted into
the fluid line coupling assembly, the spring clip 42 will engage on
side of the abutment on the cooler line end portion to prevent it
from being withdrawn, and the O-ring 40 will bear against the
tubular portion below the abutment to prevent leakage.
A cross drilled ball seat member 50 is secured to end of the
passageway 38.4 remote from the spring clip 42 by force fit or any
other suitable manner. The ball seat member 50 has a ball seat 50.1
which a ball 52 may rest against. The ball 52 is normally forced
into contact with the seat by a compression spring 54, the spring
54 being retained within ballcheck sleeve 56. The sleeve 56 bears
against a shoulder 38.6 in the body 38 to hold the spring 54 and
ball 52 in their proper operating condition. A thermal actuator 60
is secured to the end of the ball seat member 50 at a location
spaced away from the seat 50.1 by threads, a press fit, etc.
The thermal actuator has a piston 62 which may contact the ball 52.
In operation, the piston of the thermal actuator, which may be of
the type sold by Caltherm of Columbus, Ind., for example, will
raise the ball 52 away from the seat when the fluid temperature is
above a certain point, permitting flow through the cross drilled
apertures 50.2, past the ball 52, and then into line L.sub.1.
The design described above allows for any type of attachment to a
mating port. The mating plate can be designed to any customer
specification, and the assembly can also be incorporated into a
stand-alone housing that could be connected in-line with the
transmission cooling lines utilizing quick-connects.
In order to understand the operation of the cooler bypass assembly,
it will be assumed that it is mounted on an automatic transmission.
It is well known in the art that the fluid within a transmission
has a desired operating temperature, typically in the range of
175-225.degree. F. depending upon make and model. When the
automatic transmission fluid (ATF) is below this temperature, the
transmission will have operating inefficiencies due to its higher
viscosity, which causes the vehicle to consume more fuel. At
temperatures above the desired operating temperature, the life of
the ATF will begin to plummet. In order to prevent loss of life of
the ATF, the transmission fluid is passed through a cooler, which
may be in the automotive radiator. Alternatively, if the vehicle is
equipped with a trailer towing package, the transmission fluid is
passed through an external cooler. At normal ambient temperature
ranges, it typically takes only about 10 minutes for the ATF to
reach its desired operating temperature, However, in extreme
conditions, for example a vehicle having an external cooler which
is not towing a trailer, and when the temperature is quite cold,
for example 10.degree. F., the ATF fluid may never attain the
desired operating temperature range if passed through a cooler. In
any event, passing the ATF through a cooler decreases the
efficiency of a vehicle until the desired operating temperature has
been achieved.
In operation, the cooler bypass assembly will be secured to the
transmission with the inlet port 10.7 in communication with the ATF
outlet port indicated by the arrow P.sub.o and with the outlet port
10.8 in communication with the AFT inlet port P.sub.i. When the
vehicle is initially started the ATF will be at ambient
temperature, for example 55.degree. F. At this temperature, it will
flow through port P.sub.o into the inlet port 10.7m and then
through the transverse passageway 10.6, and then out of the
assembly through outlet port 10.8 and inlet port P.sub.i. It will
not flow to the cooler, as the temperature is not high enough to
cause the thermal actuator to expand and raise the ball 52 against
the spring pressure to permit ATF flow past the ball 52 and to the
cooler represented graphically at C in FIG. 2. If for any reason
the cooler restricts flow, the ballcheck 12 will open up, allowing
bypass of the cooler.
Referring now to FIGS. 13A-28, there are depicted several
additional aspects of a check valve which can be used in
replacement of the ball 12, the spring 14, and the ball check
retainer 16 in the cooler bypass housing 10 or used in any other
fluid component to uni-directionally control fluid flow through a
bore or passageway.
In each of these new aspects, the ball check retainer 16 and the
spring 14 will be as substantially shown in FIG. 8. The spring 14
may be provided by itself in the bore in the housing or in a spring
cage 70 shown in FIG. 13. Therefore, for clarity, the ball check
retainer 16 and the spring 14 will not be shown in all of the FIGS.
13A-23.
In normal operation, when the check valve is not moved to an open
position by the actuator and fluid is flowing into the high
pressure inlet of the housing, the high fluid pressure overcomes
the spring force of the spring 14 and moves the ball or movable
element of the valve away from the valve seat in the housing bore.
However, substantially immediately after the ball 12 begins to
move, high pressure fluid begins to flow around the ball 12 and
into the bore of the housing. This results in an immediate
substantial equalization of the pressure on both sides of the valve
ball 12 which allows the spring 14 to expand and force the ball 12
back in the direction of the valve seat. The result is a modulation
or flutter of the ball 12 relative to the valve seat which can
create objectionable noise in the operation of the bypass
assembly.
As shown in FIG. 13A, the movable element 72 of a valve 74 may be
in the form of a ball, or a cylindrical piston with a piston face
or a movable body disposed within the housing bore having a conical
seat complimentary to the shape of the valve seat 10.63. Therefore,
by example only, the movable element or body 72 of the valve 74
will be described hereafter as a ball 72.
The valve 74 includes a second bore 76 of a larger diameter than
the bore 10.62 which extends from a shoulder or surface 78 which
carries the valve seat 10.63. The second bore 76 transitions
through a second shoulder or surface 80 to a third larger bore
portion 10.61. The second shoulder 80 acts as a stop for the spring
cage 70.
In normal operation, prior to the introduction of pressurized fluid
into the assembly, the spring 14 will exert a force against the
ball 72 which will hold the ball 72 firmly against the at least the
first valve seat 10.63. This blocks the flow of fluid through the
bores 10.62, 76 and 10.61.
The spring cage 70 includes an oscillation dampening construction
which, in this aspect, includes at least one or a plurality of
apertures 82 formed through at least an inner surface 71 of the
cage 72 and arranged in a circumferential pattern at a position
spaced from one end of the spring cage 70 to define a modulation
flow zone denoted by reference number 84 in FIGS. 13A and 13B. The
apertures 82 may take any form, such as the elongated slots shown
by example only in FIGS. 13A and 13D, but which may be open
entirely through the wall of the cage 70 or just a groove in the
wall of the cage.
When fluid of a sufficiently high pressure is introduced through
the inlet port of the housing, the fluid pressure will overcome the
force of the spring 14 thereby urging the ball 72 away from the
valve seat 10.63. This initial movement of the ball 72 is in a
first, controlled leak liftoff zone denoted generally by reference
number 86 which extends from the second shoulder 80 to the
beginning of the flow apertures 82. In the controlled leak liftoff
zone 86, there is little or only a minimal amount of fluid flow
past the ball 72 and through the apertures 82. When the
circumference or largest diameter portion of the ball 72 reaches
the beginning point or edge 83 of the apertures 82, shown in
phantom in FIG. 13A as reference number 73, fluid begins to flow
around the outer surface 75 of the ball 72 as shown by reference
number 83 in FIG. 13C and into and through the apertures 82 in the
spring cage 70 back into and through the remainder of the bore
10.61 in the direction of the arrows in FIG. 13A. Point 83 defines
the start of the second modulated flow zone 84 in which fluid flows
from bore 10.62 past the ball 72 and through bore 10.61.
A portion of the fluid interim the apertures or slots 82 can flow
completely through the apertures 82 and over the exterior surface
of the spring cage 70, if any such space exists, before re-entering
the main bore 10.61 flow.
During such movement of the ball 72, fluid passes through the bore
10.62 and into the bore space between the first valve seat 10.63
and, also into the liftoff zone 86. This creates a volume of
pressurized fluid between the ball 72 and the valve seats 10.63
which acts as a damper to modulate any reverse movement of the ball
72 toward the valve seat 10.63. While there may be a few
thousandths of inches of axial movement of the ball 72, the cushion
of fluid acting on one end of the ball 72 substantially maintains
the ball 72 in the modulated flow zone 84 and prevents contact of
the ball 72 with the valve seat 10.63 until fluid flow is
discontinued.
In another aspect of a valve 90 as shown in FIGS. 14, 15, 16A and
16B, the valve 90 includes an insert or body 92 in the form of a
cylindrical body which carries the bore 10.62, the valve seat
10.63, the shoulder 78, the second bore 76, the second shoulder 80
and a third bore 90.
The body 92 may be mounted in the housing 10 by press fit, or by
other mounting means. The body 92 receives the spring 14, the
spring cage 70, and one end of the ball check 16. In this aspect,
one or more longitudinally extending flutes or flow channels, with
three flutes 94, 96, and 98, as shown by example only, are formed
within the interior of the body 92 and extend substantially from
the second shoulder 80 to one end 100 of the body 92. The flutes
94, 96, and 98 are similar in function as the apertures 82 between
the exterior of the spring cage 70 and the valve 90 of the bore
10.61 described above and shown in FIG. 13A and define flow paths
for pressurized fluid from the first end or bore 10.62 or through
the bore 10.61 when the ball 72 has been moved into the modulated
flow zone 84 as described above.
Referring now to FIG. 17, there is depicted another aspect of a
check valve 140 which may be employed in any check valve
application that requires one-way directional flow through a bore
or passageway, such as in the bypass cooler application described
above and shown in FIGS. 1-12.
The check valve 140 includes a movable member 72, such as a ball 72
described by way of example only, a biasing spring 14 operative to
engage and normally bias the movable member or ball 72 into sealed
engagement with a valve seat 142 formed in a first end 144 of a
spring cage 146 which captures the ball 72 and the spring 14. A
second end 148 of the spring cage 146 is turned inward as a flange
or stop to retain the spring 14 and the ball 72 within the interior
of the spring cage 146.
The spring cage 146 with the integrally mounted ball 72 and spring
14, and integral, one-piece valve seat 142 may be inserted as a
cartridge or insert into a fluid bore in an orientation such that
the spring 14 normally biases the ball 72 into sealed engagement
with the valve seat 142 in an opposite direction from the desired
fluid flow through an inner bore 150 formed with the spring cage
146.
Apertures, such elongated slots 82, are formed in a circumferential
band in the sidewall of the spring cage 146 spaced from the first
end 144. The leading edges 83 of the slots 82 are positioned along
the length of the sidewall of the spring cage 146 to define a first
substantially no-leak zone 86 and second modulating zone 84 as
described above. When fluid pressure acting on the ball 72 to move
the ball 72 in a direction overcoming the biasing force exerted by
the spring 14, the ball 72 initially moves through the substantial
no-flow liftoff zone 86 in which fluid flow through the interior of
the spring cage 146 remains substantially blocked. Only when the
circumference or largest diameter portion of the ball 72 reaches
the leading edge 83 of the slots 82 at the start of the second
modulation flow zone 84, does fluid begin to flow past the exterior
surface of the ball 72 through a portion of the slots 82 and then
through the remaining portion of the bore 150 in the spring cage
146 and then onto the main bore in which the cage 146 is mounted.
The fluid flowing through the open first end 144 of the spring cage
146 through the first distance or zone 80 creates a volume of fluid
which maintains the ball 72 in the second modulation flow zone 84
and out of contact with the valve seat 142 as long as fluid is
flowing, as described above.
In the following aspects shown in FIGS. 18-23, the oscillation
dampening construction is disposed directly within a bore or fluid
passage in valve housing and moves relative to a valve seat also
integrally formed in the valve housing. It will be understood that
the oscillation dampening construction shown in FIGS. 13-17, which
utilize an insert or body inserted into a fluid passageway in valve
housing, can also be employed directly within the fluid passageway
of valve housing without the insert. Likewise, the following
aspects of the oscillation dampening construction which are
described and illustrated, by example only, as being employed
directly within the fluid passage of a valve housing, could also be
employed in an insert or body inserted into a fluid passageway in a
valve housing
In another aspect shown in FIG. 18, a conical shaped valve seat 102
is formed between one end of the bore 10.62 and a second larger
diameter bore 104. The bore 104 continues at a constant diameter
substantially along the length of the valve. Flutes 106 and 108,
with two flutes being shown by example only in the cross sectional
view depicted in FIG. 18, are formed in a cylindrical body similar
to body 92 or directly in the housing. The flutes 106 and 108 open
to the bore 104. The flutes 106 and 108 may have, as shown in FIG.
18, a tapered draft angle configuration having an expanding
diameter from the beginning of the modulation zone 84 to the
opposite end of the bore 104.
The separate flutes 106 and 108 shown in FIG. 18 need not be
separately formed in the body 92 or the housing bore as such flutes
or draft angles may be a normal part of the casting process and can
be employed to form the flow paths around the movable element of
the valve. A machined bore with sufficient diameter starting at the
beginning of the modulation flow or zone 84, would accomplish the
same purpose.
A modification of this design is shown in FIGS. 19 and 20 in which
the beginning of the modulation zone 84 is defined by a shoulder
110 which may be a conical shoulder which forms a tapered
transition between the second bore 104 and a larger diameter bore
112 which extends to the opposite end of the valve.
In another aspect shown in FIGS. 21 and 22, the flutes 106 and 108
are replaced by one or more secondary bores 116 which extend along
the length of the constant diameter second bore 104 from a
transition surface 114 which is located at the initial modulation
point of the modulation zone 84. One or more secondary bores 116
also will form flow paths through the modulation zone 84 and the
main second bore 104.
As depicted in FIG. 23, a no-flow zone 132 and the beginning of the
modulation zone 84 may be formed simply by cross drilling a
transversely extending bore 130 into fluid communication with the
through the second bore 104 to create the no-flow zone 132 and the
modulation zone 84 in the bore.
Referring now to FIGS. 24 and 25, there is depicted another aspect
of a check valve employable in uni-directional flow applications.
The check valve 210 will be described by way of example only as
usable in the cooler bypass assembly 10 described above and shown
in FIG. 1.
In the aspect, the check valve 210 is mounted in the transverse
bore fluidically extending between the first and second fluid flow
passageways SA.sub.1 and SA.sub.2 as described above. The
transverse bore has a first smaller diameter portion 10.61 and a
second larger diameter portion 10.62. A conical valve seat 10.63 is
formed at the intersection of the first and second bore portions
10.61 and 10.62.
The check valve 210 includes a movable member 212 which will be
described hereafter as being in the form of a spherical ball. It
will be understood that other shapes may also be employed as the
movable member as described in previous aspects of the check
valve.
The spring 14 or biasing member is mounted on a spring retainer
214. The spring retainer 214 is a one-piece member having an
enlarged first end 216 which seats against an end surface of a plug
218. A seal member 220, such as an O-ring, sealingly couples the
plug 218 into and closing the transverse bore section 10.62 at a
position beyond the transversely extending fluid flow passageway
SA.sub.1.
The spring retainer 214 has a shoulder 222 spaced from an opposite
second end 224. The shoulder 222 serves as a seat for one end of
the spring 14. A bore 226 extends through at least a portion of the
spring retainer 214 from the second end 224.
The check valve 210 includes means for dampening the movement of
the movable valve member or ball 212 and to prevent oscillation of
the ball 212 in all directions within the bore section 10.62. The
dampening means includes a slidable member 230 having an elongated
rod or stem 232 slidably disposed within the bore 226 in the spring
retainer 214. A piston 234 extends from one end of stem 232 and is
disposed externally of the second end 224 of the spring retainer
214. The piston 234 has a first diameter portion 236 and a second
larger diameter portion 238, by example only. A seat or spherical
recess 240 is formed in an end face 242 in the enlarged portion 238
of the piston 234. The recess 240 is sized to snugly receive and
capture the movable valve member or ball 212 to prevent oscillation
of the ball in all directions within the bore section 10.62.
A shoulder 244 is formed as a second spring seat between the first
diameter portion 236 and the enlarged diameter portion 238 of the
piston 234. The spring 14 is thus captured between the seat 222 on
the spring retainer 214 and the seat 244 on the piston 234.
An end portion of the spring retainer 214 extending from the second
end 224 to the seat 222 has an outer diameter to concentrically
receive one end of the spring 14 to center and retain the spring 14
in position.
In use, when the check valve 210 is in the normal closed position
preventing fluid flow from the first bore section 10.61 through the
second bore section 10.62 and into the first fluid flow passageway
SA.sub.1 of the body 10, the spring 14 will extend the piston rod
232 relative to the spring retainer 214 to bring the recess 240 in
the piston head 234 against the movable valve member or ball 212
thereby securely sealing the ball 212 against the valve seat
10.63.
When the pressure of the pressurized fluid flowing through the
first bore section 10.61 exceeds the force of the spring 14, the
pressurized fluid will force the movable valve member or ball 212
away from the valve seat 10.63. The movable valve member or ball
212 moves to the right, in the cross sectional view of FIG. 27
thereby moving the piston 234 and the piston rod 232 into the bore
226 in the spring retainer 214 and compressing the spring 14.
Pressurized fluid then flows past the ball 212 over the valve seat
10.63 and into the bore section 10.62 and from the bore section
10.62 into the first fluid passageway SA.sub.1.
Since pressurized fluid is now on both sides of the piston head 234
and ball 212, any oscillation of the ball 212 due to pressure
equalization which would tend to move the ball back towards the
valve seat 10.63 resulting in objectionable flutter and noise is
prevented by the increased effective mass of the joined movable
member 212 and the piston 230. The ball 212 is captured in the
recess 240 in the piston head 234 to make the ball 212 and the
piston 230 act as a single co-joined body. The piston 230
effectively increases the mass of the ball 212 which dampens any
oscillations of the ball 212 in longitudinal and transverse
directions within the bore section 10.62.
In addition, the area behind the piston head 234 within and around
the spring 14 will eventually be filled with pressurized fluid
since the fluid is flowing from the bore section 10.61 around the
ball 212 and the exterior of the piston head 234. The pressurized
fluid which is located behind the piston head 234 in the area of
the spring 14 also acts on the joined piston head 234 and ball 212
as an additional hydraulic dampener to prevent reverse oscillation
of the ball 212 back toward the valve seat 10.63.
A modification to the check valve 210 is shown in FIG. 26 as part
of a check valve 260. Like elements in the check valves 210 and 260
are depicted with the same reference number and will not be
described in detail except to explain the interaction of such like
members or components and any modified or additional
components.
Thus, the check valve 260 which is depicted as being mounted in the
transverse bore sections 10.61 and 10.63 of the cooler bypass
assembly housing 10, includes the spring 14 and the spring retainer
214. The bore 226 is formed in the spring retainer 214 extending
from the first end 224. The shoulder 222 is formed at a position
spaced from the first end 224 of the spring retainer 214 to serve
as a seat for the spring 14. In this aspect, the check valve 260
includes an integral or unitary movable member 262 which serves the
dual functions of the movable member or ball 212 and the piston 230
in the check valve 210 described above and shown in FIGS. 26 and
27.
The movable member 262 includes an elongated stem or rod 264 which
slidably fits within the bore 226 of the spring retainer 214. A
first enlarged diameter portion 266 extends from one end of the
stem or piston rod 264 and has an outer diameter sized to fit
within the inner diameter of the spring 14 to center the spring 14
between the first seat 222 formed on the spring retainer 214 and a
second seat 268 formed by a shoulder on the movable member 262
between the outer diameter of the first enlarged portion 266 and an
outer diameter of a dumbbell or hemispherical shaped head 270. The
head 270 has a spherical end portion 272 which sealingly engages
the valve seat 10.63 to block fluid flow through the bore sections
10.61 and 10.62 in a normally closed position of the check valve
260.
It will be understood that the stem 264, while unitarily joined to
the head 270 may be a separate component from the head 270 and
fixed thereto in a slip or friction fit as well as being joined to
the head 275 by welding, or other joining means. The stem 264 and
head 270 may also be unitarily cast or molded as part of a unitary
movable member 262.
The movable member 262 provides the same function as the ball 212
and the piston 230 in the check valve 210 in that it dampens
movement of the head 270 to prevent oscillation of the head 270 in
both directions within the bore 10.4 and 10.62 as pressurized fluid
flows through the bore sections 10.61 and 10.62 into the first
fluid flow passage SA.sub.1.
It will be further understood that the oscillation dampening
constructions shown in FIGS. 24-26 are illustrated by example only
as being disposed within fluid passageway of a large valve body;
but could also be disposed within an insert housing disposed within
a bore in a fluid passageway in the larger valve housing.
Referring now to FIG. 27, there is depicted another aspect of a
cooler bypass assembly 160. The assembly 160 includes a body 162
which may be formed of a one-piece casting, a machined body, or
multiple pieces joined together by welds, fasteners, or
combinations thereof.
The body 162 has a first fluid flow passage SA.sub.3 with a through
bore extending between a first coupler 38 and a second coupler 39.
The thermal valve assembly described above may be mounted in the
bore in the first fluid flow passage SA.sub.3.
The couplers 38 and 39 are quick connectors where the coupler 38 is
adapted for receiving an enlargement 166 on a profiled end surface
of a pipe 167 to connect the inlet of the first fluid flow passage
SA.sub.3 which can be coupled to the outlet or discharge of a fluid
flow fitting on the machinery carrying the coolant fluid.
The coupler 39 similarly receives an enlargement 168 on a profiled
end surface of a pipe or conduit 170 in a snap-in connection to
couple the pipe 170 to the outlet end of the first flow passageway
SA.sub.3 in the body 162.
A second fluid flow passageway in the form of a bore mounted in the
body 162 is denoted by SA.sub.4. The second fluid flow passageway
also includes couplers 28.2 in the form of quick connectors which
are mounted in or otherwise connected to the couplers 28.2 or
coupled directly to the body 162. The coupler 28.2 is adapted for
receiving an enlargement 176 on a profiled end surface of a pipe or
conduit 178 which receives fluid, such as from an outlet of a
cooling device or cooler. The other coupler 28.2 receives a similar
enlargement 180 on a profiled end surface on a pipe or conduit 182
connected to a coupling on a fluid carrying component. The second
fluid flow passageway SA.sub.4, is adapted, for example, for
receiving coolant flow from the cooler, not shown, through the pipe
178 and passing the fluid through the pipe 182 back to the
machinery which utilizes the coolant fluid.
The body 162 also includes a transverse or bypass bore housed in a
body section 184. The body section 184 may house a check valve, as
described above, to control one way directional flow of fluid
between portions of the first and second fluid passageways,
SA.sub.3 and SA.sub.4, dependent upon the position of the thermal
valve mounted in the first fluid flow passageway SA.sub.3, as
described previously.
The pipes 167, 170, 178 and 182, may be constructed of any fluid
carrying material suitable for a particular application. The pipes
167, 170, 178 and 182 may be rigid or flexible. Thus, the pipes
167, 170, 178, and 182 themselves may be used to mount the body 162
between the cooler, not shown, and the machinery which carries the
coolant fluid, also not shown.
In addition, the body 162 includes a first pair of flanges 186 as
well as transverse flanges or ribs 188. Bores 190 may be formed in
any of the flanges or ribs to enable mechanical fasteners to be
employed to fixedly mount the body 162 to any surface, including
surfaces or components adjacent to the machinery carrying the
coolant fluid, rather than or in addition to a connection directly
on the machinery carrying the coolant fluid, or not directly to the
fluid flow ports as described in the first aspect of the cooler
bypass assembly.
Referring briefly to FIG. 28, there is depicted an example of the
ball check 16 and the spring 14. The movable element of the valve,
in this aspect, is depicted as a hollow, cylindrical body 120
having a conical seat surface 122 at one end which is configured to
mate with a complimentary conical seat, such as conical valve seat
102 described above. The edge 124 of the body 120 at one end of the
conical seat 122 defines the outer diameter of the cylindrical body
120 around which fluid begins to flow through the flutes 106, 108
or apertures 82, as described above, when the surface 124 reaches
the beginning of the modulation zone 84.
* * * * *